US2585348A

US2585348A - Pump-motor hydraulic system, including multiple motors and their controls

Info

Publication number: US2585348A
Application number: US751712A
Authority: US
Inventors: Robinson James
Original assignee: Vickers Inc
Current assignee: Vickers Inc
Priority date: 1947-06-02
Filing date: 1947-06-02
Publication date: 1952-02-12
Anticipated expiration: 1969-02-12

Description

Feb. 12, 1952 J 0 so 2,585,348

PUMP-MOTOR HYDRAULIC SYSTEM, INCLUDING MULTIPLE MOTORS AND THEIR CONTROLS Filed June 2. 1947 FIG.3

FIG. 4

INVENTOR.

- JAM ES ROBINSON ATTORN EY Patented Feb. 12, 1952 PUMP-MOTOR HYDRAULIC SYSTEM, m-

cwnmc. MULTIPLE MOTORS AND THEIR CONTROLS James Robinson, Huntington Woods, Micln, as-

signor to Vickers Incorporated, Detroit, Mich, a corporation of Michigan Application June 2, 1947, Serial No. 751,712

7 Claims.

This invention relates to power transmissions, particularly to those of the type comprising two or more fluid pressure energy translating devices, one of which may function as a pump and another as a fluid motor.

The invention is generally concerned with a system of this character for driving a load device requiring low torque at high speeds and high torque at low speeds.

In particular, the invention is concerned with a system of this type at which a very high torque is demanded at low speed and a very high speed at low torque, and wherein the intermediate torque and speed between these extreme conditions are relatively unimportant.

In the past, conventional hydraulic transmissions of this type required a large hydraulic motor for delivering high torque which in turn necessitated the use of a large pump for driving the motor at extremely high speeds.

It is an object of this invention to provide a hydraulic power transmission system which en ables the use of smaller units for the extreme conditions mentioned, thereby reducing the overall cost and weight.

Further objects and advantages of the present invention will be apparent from the following description, reference being had to the accompanying drawing wherein a preferred form of the present invention is'clearly shown.

In the drawing:

Figure 1 is a diagrammatic view of a hydraulic power transmission system embodying a preferred form of the present invention.

Figure 2 is a diagrammatic view of two of the control elements shown in Figure 1, but showing the same in a different operating position.

Figure 3 is a simplified schematic view of the hydraulic system shown in Figure 1 and tracing the course of fluid therein when the control parts are in the position as shown in Figure 1.

Figure 4 is a view corresponding to that of Figure 3, but showing the course of fluid flow when the control parts are in the position shown in Figure 2.

Referring now to Figure 1, there is shown a reversible pump It, the displacement of which may be manually varied and which may be driven by an electric motor or other prime mover (not shown). The pump I is adapted to supply pressure fluid to a pair of fixed displacement rotary fluid motors l2 and I4 which are mechanically coupled to each other and which are also connected to a drum or hoist l8 for the purpose of driving the same. The motor l2 has a greater displacement per unit of time than that of motor A circuit is provided connecting the pump Ill and motors l2 and I4 continuously in parallel. This circuit is controlled by a directional control valve l8 which remains in the position shown in Figure 1 when the pressure in the circuit is low. When the pressure in the circuit increases to a value determined by the setting of a pressure responsive pilot relief valve 20, the control valve I8 is operated to a position shown in Figure 2. A delivery conduit 22 connects the outlet of the pump ill to the inlet of the motor l2. The delivery conduit 22 is also connected to a control port 23 at the left end of valve I8 by means of a branch conduit 24, to a control port 26 of the pilot valve 20 by means of a branch conduit 28, and to a pressure port 30 of the control valve l8 by means of a branch conduit 32 of the conduit 28. The control valve I6 is also provided with

operating ports

34, 36 and 38, the former of which is connected by a return conduit 39 to the pump in and to the outlet of the motor I2 by a branch conduit 40. The port 36 is connected to the outlet of the motor l4 by a conduit 42 and the port 38 is connected to the inlet of the motor l4 by a conduit 43. Due to the fact that the pump l6 and the motors I 2 and I4 are connected to each other in a closed system, a replenishing pump 44, which is connected to a tank 46 by a conduit 48, supplies fluid to either the delivery or

return conduit

22 or 39 by means of a branched conduit 48.

Duplicate check valves

56 and 62 are incorporated in the branches of the conduit 48.

Suitable relief valves

54, 56 and 58 are incorporated respectively in the

conduits

22, 39 and 48. The

relief valves

54, 56 and 58 exhaust excessive pressure fluid, respectively, to the conduits 38. 22, and to the tank 46, respectively, by conduits 60. 62 and 64. a

A fluid operated valve spool-65 of the control valve I8 is provided with an extreme right end land 66, a center land 68, and a land 10 to the left of land 68. The left end of the spool 65, indicated generally by the numeral 12, is adapted to be in continual communication with conduit 22 by means of the branch conduit 24 and port 23. The land 66 which has a greater surface area than the left end portion 12 of the spool 65 is only in communication with conduit 22 when the valve 26 is operated in response to predetermined increases in pressure in conduit 22. For this purpose, the right end of the valve I8 is provided with a port I4 in communication with land 4! which is connected to an outlet port ll of the valve 20 by a conduit 12.

The valve 24 is provided with a spool ll biused to the position shown by means of a spring '2 of predetermined resistance. In the position shown, the spool 20' blocks communication between the port 2' and the port", but upon pressure increases in conduit 22, as determined by the resistance of spring 82, the spool 8| shifts upwardly to connect the

conduits

22 and 28 and the port 2 to the port It and the conduit 14. The valve 2. is vented by means of a conduit 44 connected to a venting port IQ of the valve 24 and to the tank 46.

It should be noted that the delivery and return conduits 22 and 3!, respectively, of the pump II which are connected to the inlet and outlet of the motor I2, and likewise the inlet and

outlet conduits

42 and 43, respectively, of motor I4 alternate asdelivery and return and as inlet and outlet conduits depending upon the direction of rotation of the pump II.

Referring now to Figure l, for a hoisting operation, with the pump III being operated in a direction making conduit 22 the delivery conduit and conduit 39 the return conduit, pressure fluid is delivered by conduit 22 to the inlet of motor I2, to the pressure port ill of valve I! by

conduits

28 and 32 and to the control port 26 of valve 24 by conduit 28. Pressure fluid is also delivered to the port 22 of valve I8 by means of the conduit 22 and branch conduit 24. Pressure fluid entering the port 23 of the valve I8 contacts the portion 12 of the spool 65 and shifts the latter to the position shown. As long as the pressure in conduit 22 remains below the setting of the valve 20, the spool 65 is maintained in the position shown. Although conduit 22 is in communication with the outlet of the motor I4, as the motor I2 is capable of delivering a greater torque than motor I 4, the former motor will drive the latter as a pump. The displacement from motor I2 is delivered to the inlet of the motor I4 by the conduit 40 connected to the outlet of motor I2, conduit 38,

ports

34 and 28 of the control valve I8, and the inlet conduit 43 of the motor I4. The displacement from 'motor I4 is delivered by means of the

ports

38 and 30 of the valve I8 and the

conduits

32 and 28 to the delivery conduit 22 of pump I and thence to the inlet of the motor l2. As motor I2 has a greater displacement than motor I4, the discharge from motor I2 in excess of the consumption of motor I4 is returned to the pump III by means of the return conduit 29. Consequently, the drum I6 will be driven solely by the motor I2. The speed at which the drum is driven by the motor I2 will be commensurate with the total displacement of pump It being delivered to the motor I2 plus thetotal displacement of motor I4 added to the pumpdelivery, pump Ill and motor I4 thus acting in parallel to supply the motor I2. The torque delivered is low, being that of motor I2 less that required to operate motor I4 as a pump. The driving speed will be high because the displacement of motor I4 is added to the supply of fluid flowing to the inlet of the motor I2 from pump III.

When the torque demand reaches the opposite extreme, the pressure in conduit 22 will also increase. When it reaches a value determined by the setting of spring 82 of valve 20, the spool ",will shift upwardly to connect the

conduits

22 and 28 and the

ports

28 and 18 of the valve 24 to the conduit I8 and the port 14 of the valve II. The positions of the control valve II and the pilot valve 24 will now be as shown in Figure 2. With an equal pressure existent at both ends of the valve spool 45, the latter will shift leftwardly due to the greater surface area of land $8. With the valve spool ll shifted leftwardly, the port 20 of the valve II will be connected to port 38 thereof and the port 24 will be connected to the port 24. Pressure fluid from the pump II in addition to being delivered to the inlet of the motor I2 is now delivered by

conduits

22, 28 and 32, the valve ports II and ll, and the conduit 43 to the inlet of the motor I4. Fluid displaced from the motor I2 through conduit 44 flows back to the pump I. through the return conduit 29 while the displacement from the motor I4 also flows to the return conduit 32 of pump it by means of conduit 42, and the

ports

28 and 34 of valve I8. As the total displacement of the pump III is now divided between both of the motors, the speed of the drum It will be proportionately decreased. However, the motor I4 will now deliver torque to the drum II in addition-to the torque delivered by the motor I2. Consequently, although the speed of the drum is proportionately decreased by the subtracting of the consumption of motor I4 from the fluid displacement of the pump It, the torque delivered is increased to the combined delivered torque of both motors. If the rotation of pump III is reversed for a lowering operation, the supply conduit 29 becomes the delivery conduit and the delivery conduit 22 becomes the return conduit. Likewise, the inlets and the outlets of the motors I2 and I4 are reversed as to the operation of said motors. Fluid is now delivered by the pump I0 through the

delivery conduits

39 and 40 to the inlet of motor I2 to reverse the driving direction of motor I2. Although conduit 38 is open to the outlet of the motor [4, the motor I2 will drive the motor I4. The inlet of the motor I4 is supplied with fluid being displaced from motor I2 by means of the

conduits

22, 28 and 32, the

ports

20 and 34 of valve I8, and the conduit 42. Fluid displaced from the motor I4 is added to the supply of fluid from the pump I 0 and directed to the inlet of motor I2 by means of the conduit 43, the

ports

38 and 34 of the valve I8, and conduit 39. There will be a continual pressure in the conduit 22 and so a negligible pressure in conduit 39 regardless of whether a hoisting or lowering operation is taking place. The pressure exists in the direction of the load and due to the fact that the load on both motors I2 and I4 is in the same direction and con- 55 tinually biases the motors in that direction, re-

gardless of a hoisting or lowering operation, there will be a continual pressure in the conduit 22. The amount of the pressure is dependent upon the load. The setting of the valve 20 is accord- 60 ingly determined by the pressure which a high load will create in order to connect both motors to the load and thus utilize their combined torque output.

In a lowering operation, the load actually drives 0., the motors and the motors tend to drive the pump and overhaul the same. When the load is increased, the tendency to overhaul the pump is increased. The pump continually opposes this tendency to overhaul and consequently any in- 70 crease in load increases the pressure in the conduit 22.

Thus, in a lowering operation, if the load is increased to an extent creating a pressure in conduit 22 suflicient to overcome the resistance 76 01' valve 20, the valve 20 will be operated to connect the

conduits

22, 28, and 26 to conduit I8 and shift the valve spool 65 of the valve Hi to the position shown in Figure 2. Conduit 39 is now connected to the inlet of motor l2 and to the inlet of motor I4 by means of

ports

34 and 36 of valve l8 and conduit 42. The outlet of the motor I is connected to conduit 22 by conduit 43,

ports

38 and 30 of valve l8 and

conduits

32 and 28. The outlet of motor I2 is connected to conduit 22. The speed of the drum is decreased because the conduit 39, connected to the outlet of the pump it, is connected to the inlet of both motors, thus dividing its displacement.

It should thus be noted that the transmission provided is an economical and eilicient means of driving a load device at high speed with low torque and with high torque at low speed. The speed of the larger motor at low torque is increased by adding to the pump delivery the displacement from the smaller motor. The torque delivered is low because only the one motor drives the load device at high speed and the torque is further decreased by that one motor having to drive the smaller motor as a pump.

The torque delivered to the load device is increased by adding the torque delivery of the smaller motor for driving the load device at low speed. The speed is low because the pum flow is proportionately divided between the two motors.

It should also be noted that the extreme low and high speed of the load device and the extreme low and high torque delivered thereto may be varied over a wide range by careful preselection of the displacement and torque delivery of the motors.

While the form of embodiment of the invention as herein disclosed constitutes a preferred form, it is to be understood that other forms might be adopted, all coming within the scope of the claims which follow.

What is claimed is as follows:

1. In a hydraulic power transmission system the combination of a pump unit A, a motor unit B and a combination motor-pump unit C, unit B having a greater displacement than unit C and units B and C being mechanically coupled to each other and to a load device, a circuit connecting the units and means for selectively establishing two circuit connections, on withunits A and C in parallel with each other to operate unit B as a motor and unit C as a pump and the other with unit A operating B and C in parallel as motors.

2. In a hydraulic power transmission system the combination of a pump unit A, a motor unit B, and a combination motor-pump unit C, unit B having a greater displacement than unit C and units B and C being mechanically coupled to each other and to a load device, a circuit establishing a parallel connection of the units and means for selectively reversing the connections of one of the units B and C to cause the unit C to either assist or oppose the unit, B in driving the load device.

3. In a hydraulic power transmission system the combination of a pump unit A, a motor unit B, and a combination motor-pump unit C, unit B having a greater displacement than unit C and units 3 and C being mechanically coupled to each 6 nections, on with units A and C in parallel with each other to operat unit B as a motor and unit C as a pump and the other with unit A operating B and C in parallel as motors.

4. In a hydraulic power transmission system the combination of a pump unit A,'a motor unit B and a combination motor-pump unit C, unit B having a greater displacement than unit C and units B and C being mechanically coupled toeach other and to a load device, a circuit establishing a parallel connection of the units and pressure responsive control valve means for selectively reversing th connections of one of the units B and C to cause the unit C to either assist or oppose the unit B in driving the load device.

5. In a hydraulic power transmission system the combination of a pump unit A, a motor unit B and a combination motor-pump unit C, unit B having a greater displacement than unit C and units B and C being mechanically coupled to each other and to a load device, a circuit connecting the units and means for selectively establishing at predetermined low pressures one circuit connection and at a predetermined increase in pressure another circuit connection, the one at, low

pressures establishing units A and C in parallel with each other to operat B as a motor and C as a pump and the one at high pressure establishing units B and C in parallel with unit A operating both unit B and unit C as motors.

6. In a hydraulic power transmission system the combination of a. variable displacement pump unit A, a motor unit B and a motor-pump unit 0. units B and C both being of the fixed displacement type and unit B having a greater displacement per unit of time than unit C, the units B and C being mechanically coupled to each other and to a load device, a circuit including connections continuously establishing the units in parallel relationship, and means for controlling the connections for causing A and C to operate B and for causing A to operate B and C.

7. In a hydraulic power transmission system the combination of a variable displacement pump unit A, a motor unit B and a motor-pump unit C, units B and C both being of the fixed displacement type and unit B having a greater displacement per unit of time than unit C, the units B and C being mechanically coupled to each other and to a load device, a circuit including connections continuously establishing the units in parallel relationship, and pressure responsive means for controlling the connections, said means at low pressures causing A and C to operate B for driving the load device at high speed and low torque and said means at predetermined higher pressures causing A to operate B and C for driving the load device at low speed and high torque.

JAMES ROBINSON.

REFERENCES CITED The following referencesare of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 2,079,268 Wiedmann May 4, 1937 FOREIGN PATENTS Number Country Date 184,455 Great Britain Oct. 18, 1923